Geared motor and chain conveyor device

Abstract

A geared motor, in particular for a chain conveyor device, wherein the geared motor has a transmission driven by an electric motor, wherein the transmission flange (22) which receives the bearings for rotatable mounting of the driving shaft (20) of the transmission on the transmission flange (22) is centred and aligned with respect to the motor-side flange part (23), in particular by a centring spigot, against which a centring collar of the flange part (23) is placed, being configured on the transmission flange (22).

Description

[0001] Gear motor and chain conveyor

[0002] Description:

[0003] The invention relates to a geared motor, in particular for a chain conveyor device.

[0004] It is common knowledge that in a chain drive a chain is driven by a motor.

[0005] The invention is therefore based on the object of designing a robust gear motor.

[0006] According to the invention, the object is achieved in the geared motor according to the features specified in claim 1.

[0007] Important features of the invention in the geared motor, in particular for chain conveyor devices, are that the geared motor has a gear driven by an electric motor, wherein the gear flange, which accommodates the bearings for the rotatable mounting of the input shaft of the gear on the gear flange, is centered and aligned with the motor-side flange part, in particular by a centering collar being formed on the gear flange, to which a centering collar of the flange part is applied.

[0008] The advantage of this is that it allows for a quick and easy connection of the motor to the gearbox, with very precise alignment and centering achieved thanks to the centering devices. Furthermore, the externally toothed rotor shaft of the electric motor can be inserted into the internal toothing of the gearbox's input shaft, enabling a low-force or even force-free connection.

[0009] In an advantageous embodiment, a torque support area and an output flange are formed on the transmission housing, particularly in one piece, with struts and a center strut each connecting the torque support area to the output flange, with the output flange accommodating a bearing of the transmission's output shaft. This is advantageous in that a stiffened transmission of the reactive torque is enabled despite high vibration levels. Although the torque support area can be formed in one piece on the transmission housing, the struts connecting it to the output flange nevertheless enable improved transmission of the reactive forces from the output flange directly to the torque support area.

[0010] In an advantageous embodiment, a cross brace connects the center brace to the struts. This offers the advantage of simple and cost-effective reinforcement, particularly by molding the cast part.

[0011] In an advantageous design, the center strut is aligned parallel to the rotor shaft's rotational axis. This is advantageous because the torque support area does not require any additional axial length.

[0012] In an advantageous embodiment, the struts each have a non-zero angle to the center strut, in particular, they have the same angle but with different signs. This is advantageous because improved stiffening can be achieved.

[0013] In an advantageous design, the center strut is positioned in the plane spanned by the struts. This has the advantage of requiring little installation space.

[0014] In an advantageous design, the cross brace is arranged in the plane spanned by the struts. This has the advantage of requiring little installation space.

[0015] In an advantageous design, the distance between the struts increases with increasing distance from the output flange, in particular, it increases strictly monotonically. The advantage here is that effective stiffening can be achieved without requiring unnecessary installation space.

[0016] In an advantageous embodiment, the axial width of the torque support area, in particular the width of the torque support area measured parallel to the rotational axis of the rotor shaft, decreases monotonically with increasing distance from the center strut. This allows for a compact design of the torque support area.

[0017] In an advantageous embodiment, springs connect two axially spaced-apart sections of the gearbox housing. The advantage of this is that, despite the vibrations introduced by the conveyor chain via a sprocket, the gearbox is sufficiently rigid and vibrations can be suppressed.

[0018] Another advantage of the invention is that it allows for quick and easy replacement of chain links while maintaining a high level of work safety. This requires no special effort. Only the release lever and the chain stop device need to be provided.

[0019] However, since the chain stop device is attached to the gear motor, i.e., to a housing-forming part of the gear motor, no additional effort is required, yet efficient dissipation of the chain forces is still possible. This is because, during the replacement of chain links, the chain force must be transferred from the chain stop device to the sprocket through the gear motor.

[0020] In an advantageous embodiment, the chain stop device is attached to the gear motor. This is advantageous because the chain force in the gear motor can be transmitted directly to the sprocket.

[0021] In an advantageous embodiment, the geared motor comprises an electric motor whose housing encloses and / or surrounds the brake. This is advantageous because the brake does not require a separate housing, thus requiring minimal effort to enclose the brake.

[0022] In an advantageous embodiment, the sprocket engages the chain over a circumferential angle range of more than 90°, in particular less than 180°. The circumferential angle range is relative to the sprocket's rotational axis. This provides the advantage of securely holding the chain.

[0023] In an advantageous embodiment, the torque transmitted from the sprocket to the chain is regulated to a target value in the third process step, in particular to achieve a target value for the chain tension. An advantage here is that the chain can be repaired under full load, because the specified chain tension can be applied using the gear motor.

[0024] In an advantageous embodiment, the first speed threshold is lower than, in particular at least ten times lower than, the target speed. This is advantageous because the chain tension can be precisely adjusted during slow travel without overloading the chain. This is because the torque of the geared motor can be directly controlled to a target value by an inverter feeding the electric motor.

[0025] In an advantageous embodiment, the brake, in particular the toroidal coil of the brake, is essentially de-energized in the fourth method step. This is advantageous in that increased safety can be achieved by de-energizing the brake, thus causing it to engage. Furthermore, the release lever is moved to the appropriate rotational position for applying the brake. When the brake is de-energized, the toroidal coil is essentially or entirely de-energized, but the brake's signal electronics may nevertheless remain electrically supplied—particularly for supplying the sensors and their evaluation circuits.

[0026] In an advantageous embodiment, the brake has a magnetic body which has an annular recess into which an electrically energizable annular winding is inserted, in particular wherein the annular axis of the annular winding is aligned coaxially with the rotational axis of the rotor shaft, wherein the rotor shaft has external teeth or is in particular connected in a rotationally fixed manner by means of a key connection to an annular, externally toothed driver which is plugged onto the rotor shaft, wherein a disc-shaped brake pad carrier is plugged onto the driver and engages with its internal teeth with the external teeth of the driver, in particular so that the brake pad carrier is arranged displaceably in the axial direction, wherein an armature disk is arranged in the axial direction between the brake pad carrier and the magnetic body, which armature disk is connected in a rotationally fixed manner to the magnetic body and is arranged displaceably in the axial direction,wherein, when the ring winding is energized, the armature disc is drawn towards the magnetic body against the spring force generated by spring elements supported on the magnetic body and pressing on the armature disc, so that the brake pad carrier runs freely, in particular wherein, when the ring winding is not energized, the spring elements press the armature disc onto the brake pad carrier and thus the brake pad carrier is pressed on its side facing away from the magnetic body onto a braking surface which is formed on a flange part or on a sheet metal part which rests on the flange part, or on the motor housing.

[0027] The advantage here is that the brake automatically engages in the event of a power failure, i.e. it automatically switches to the safe state.

[0028] In an advantageous embodiment, the release lever is connected via a rotary joint to an axially movable bolt, wherein the release lever is supported at a pivot point which is arranged on a flange part or bearing flange of the electric motor, wherein the bolt projects through the magnet body and through a recess in the armature disk and is widened on the side of the armature disk facing away from the magnet body or is connected to a part for widening such that the bolt is axially limited by means of the widening. The advantage here is that manual release is possible. In particular, the release lever can be brought into a rotary position in which the brake is released.

[0029] In an advantageous embodiment, the release lever can be locked by a locking device of the brake, in particular on the magnet body. This is advantageous because the safe state of the brake can be fixed. In an advantageous embodiment, the housing of the electric motor, which is particularly constructed in several parts, houses not only the stator of the electric motor but also the brake, in particular with the release lever protruding through the housing into the surroundings of the electric motor. It is advantageous that the release lever can be detachably connected to the housing, in particular, thus being lockable.

[0030] In an advantageous embodiment, the brake is located at the axial end of the electric motor's rotor shaft, facing away from the gearbox. This provides sufficient clearance for actuating the release lever.

[0031] In an advantageous embodiment, springs connect a first region of the gear housing to a second region of the gear housing, in particular wherein the first region is spaced apart from the second region in the axial direction, in particular parallel to the direction of the axis of rotation of the rotor shaft, in particular wherein the springs are arranged on the outer side of the gear housing. This has the advantage that, despite the high forces transmitted through the housing, the housing can be stabilized and sufficient rigidity of the housing can be maintained. In particular, vibrations of the housing can be suppressed.

[0032] Important features of the chain conveyor device for carrying out the aforementioned method are that the chain conveyor device has a sprocket that can be driven by a geared motor and engages the chain, which is detachably connected to a chain stop device, wherein the chain stop device is connected to the housing of the geared motor, wherein the chain conveyor device has a control device for adjusting the chain tension of the chain by controlling the torque delivered to the chain by the geared motor via the sprocket, in particular wherein the geared motor can be controlled or regulated by an inverter feeding the electric motor of the geared motor such that the chain tension of the chain can be tightened to a target value by controlling or regulating the torque. It is advantageous in this case that the chain conveyor device is designed to ensure repair of the chain while at the same time ensuring a high level of safety.For this purpose, the chain stop device can be attached to the gear motor and the chain wheel is able to absorb the chain tension and hold the chain via the gear by means of the holding brake arranged on the rotor shaft of the electric motor driving the gear.

[0033] Further advantages emerge from the dependent claims. The invention is not limited to the combination of features in the claims. Further possible combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent to those skilled in the art, particularly from the problem and / or the problem posed by comparison with the prior art.

[0034] The invention will now be explained in more detail using schematic illustrations:

[0035] Figure 1 shows a schematic representation of a chain conveyor device according to the invention with a gear motor.

[0036] Figure 2 shows a side view of the gear motor.

[0037] Figure 3 shows the gear motor in side view.

[0038] Figure 4 shows the gear motor in an oblique view.

[0039] As shown in the figures, the chain device comprises a geared motor whose output shaft 3 drives a sprocket 2, the teeth of which engage in recesses of chain links of a chain 1 and which thus drives the chain 1.

[0040] Preferably, the chain 1 has a length of more than 20 meters and is used in a mining installation or mine for conveying rock, ore or coal.

[0041] The geared motor has an electric motor 30 which drives a gearbox 31, the output shaft of which acts as the output shaft 3 of the geared motor.

[0042] At the end of the rotor shaft of the electric motor 30 axially remote from the gear unit, an electromagnetically actuated brake is arranged, which acts as a holding brake for the rotor shaft 24 when the tensioning or retensioning of the chain 1 is to be carried out.

[0043] To ensure operation, the brake can also be manually released. A release lever 29 is provided for this purpose, which keeps the brake released regardless of whether its coil is energized or not.

[0044] The brake comprises a magnetic body 28 made of a ferromagnetic material and having an annular recess whose ring axis is aligned coaxially with the rotational axis of the rotor shaft and which is open toward the gearbox. A current-carrying annular winding is inserted into the annular recess of the magnetic body 28 and sealed and encapsulated with a potting compound.

[0045] An annular carrier is mounted on the rotor shaft. It has external teeth that mesh with the internal teeth of a brake pad carrier 26, which is mounted on the carrier. The carrier is connected to the rotor shaft in a rotationally fixed manner, preferably by means of a keyway. The brake pad carrier 26 is arranged on the carrier so that it can be displaced in the axial direction.

[0046] An armature disk 27 is made of ferromagnetic material and is arranged axially between the brake pad carrier 26 and the magnet body 28.

[0047] When the ring winding is energized, the armature disk 27, which is arranged in a rotationally fixed but axially displaceable manner relative to the magnetic body 28, in particular by means of bolts secured in the magnetic body 28 that protrude through recesses in the armature disk 27, is pulled toward the magnetic body 28 against the spring force generated by spring elements supported in the magnetic body 28. When the ring winding is not energized, the spring elements press the armature disk 27 onto the brake pad carrier 26, so that this brake pad carrier 26 is pressed, on its side facing away from the armature disk 27, onto a braking surface formed on the bearing flange or on a part connected to the bearing flange.

[0048] The release lever 29 is pivotally mounted to a pivot point on the magnet body 28 or on a part connected to the magnet body 28, so that during its rotational movement it makes a bolt linearly movable in the axial direction.

[0049] The bolt projects through a recess in the magnetic body 28 and through a recess in the armature disk 27. The bolt is widened on the side of the armature disk 27 facing away from the magnetic body 28 and therefore pulls the armature disk 27 towards the magnetic body 28 when the release lever is actuated. When the release lever 29 is actuated, the spring force generated by the spring elements is overcome, even when the toroidal winding is not energized. This enables manual release. The brake can only be applied when the armature disk 27 is released by a corresponding rotation of the release lever 29. This is because when the release lever 29 is turned, the bolt is moved in the axial direction and the armature disk 27 is forced towards the magnetic body 28.For this purpose, the bolt is widened at its end region facing away from the magnet body 28, in particular so that the bolt rests against the armature disk 27 with this widened end region and does not slip through the recess of the armature disk 27.

[0050] Before tensioning or re-tensioning of chain 1 is carried out, the gear motor is first switched off, i.e. chain 1 is brought to zero speed.

[0051] Then, by means of a chain stop device 4, the chain 1 is releasably connected at one of its chain links to a stationary part of the system, so that the chain 1 cannot move further there. Preferably, the chain stop device 4 is attached to the geared motor, in particular between the gearbox and the motor, so that the chain 1 is stopped by the chain stop device 4 and releasably connected to the housing of the geared motor.

[0052] After the geared motor and chain 1 have stopped, the brake is activated. This is done by operating the release lever 29 and also de-energizing the brake coil. This engages the brake and prevents the rotor shaft from rotating, which in turn, via the gear 31, also stops the output shaft 3 of the gear 31.

[0053] In this way, the chain 1 can be repaired between the sprocket 2 and the chain stop device 4. For example, an exchange, i.e., replacement, of chain links of the chain 1 in this area is possible, even if the remaining area of ​​the chain 1 is under load.

[0054] This allows the chain tension to be adjusted.

[0055] After reassembling the chain links, the chain 1 can be fully used again. This then releases the chain stop device 4 from the chain 1, thus releasing the chain 1. The brake is also released by energizing the brake coil and actuating the release lever 29.

[0056] The electric motor is flange-mounted directly to the gearbox and centered. This direct flange centering eliminates the need for a coupling, thus shortening the overall length. Flange centering means that only the gearbox-side gearbox flange 22 needs to be equipped with the appropriate centering devices, and no further adjustments are necessary on the motor side.

[0057] Due to the externally toothed rotor shaft, which only needs to be inserted into the internal toothing of the input shaft of the gearbox when connecting the motor to the gearbox, a force-free or at least low-force flange connection of the motor to the gearbox is possible.

[0058] The transmission flange 22 is further stabilized by a torque support area 40 cast onto the transmission flange 22, in particular by the transmission flange 22 being formed as a single piece with the torque support area 40. This torque support area 40 is connected to the output flange of the transmission via struts 21 and a center strut 41 arranged between the struts 21, which accommodates a bearing of the output shaft of the transmission.

[0059] The central strut 41 is aligned parallel to the rotational axis of the electric motor's rotor shaft. The struts 21 are aligned at an angle to the central strut 41, in particular, forming a non-zero angle to the central strut 41.

[0060] The angles of the struts 21 to the central strut 41 are equal in magnitude, but have a different sign.

[0061] The struts 21 span a plane in which the central strut 41 also lies.

[0062] The end portions of the struts 21 and the center strut 41 facing the electric motor are connected by means of the torque support portion 40. The other end portions open into the output flange, which accommodates the bearing for the rotatable support of the output shaft.

[0063] A cross strut, which is arranged axially, i.e. in the direction of the rotational axis of the rotor shaft of the electric motor, between the torque support area 40 and the output flange, connects the struts 21 to the central strut 41.

[0064] Thus, the torque support, in particular the torque support area 40, is rigidly connected to the output flange. For further stiffening and / or resonance suppression, springs 32 are provided, connecting two axially spaced-apart areas.

[0065] The rotor shaft 24 is rotatably mounted via a bearing which is accommodated in the bearing flange 25.

[0066] In further embodiments of the invention, the chain stop device 4 is mounted at a different position so that a longer piece of the chain can be exchanged between the sprocket 2 and the chain stop device 4.

[0067] In further embodiments according to the invention, it is also possible, after attaching the chain stop device 4, to initially operate the geared motor at a very low speed in order to tension the chain 1 in the conveyor area and only then to activate the brake in order to maintain the chain tension thus achieved, while the chain link(s) are replaced and / or exchanged in the area of ​​the chain 1 between the chain stop device 4 and the chain wheel 2.

[0068] The brake is located in the motor housing. Thus, the brake is surrounded and protected by the motor housing.

[0069] The input shaft 20 of the gearbox has an external toothing at its end facing the electric motor and / or the brake, with which the input shaft 20 is inserted into an internal toothing of the rotor shaft 24. This allows a high torque to be transmitted and compensates for any misalignment of the shaft 20 with the rotor shaft 24. For this purpose, the teeth of the internal toothing and / or the teeth of the external toothing are preferably crowned.

[0070] In order to align the rotational axes of the input shaft 20 as precisely as possible with the rotational axis of the rotor shaft 24 when connecting the electric motor 30 to the gearbox 31, the gearbox flange 22, which accommodates the bearings for the rotatable mounting of the input shaft on the gearbox flange, is centered and aligned with the motor flange, i.e., a flange part 23, by forming a centering collar on the gearbox flange 22, against which a centering collar of the flange part 23 is applied. This enables highly precise alignment. The tooth coupling formed by the internal and external gearing compensates for residual tolerances.

[0071] As shown in Figure 2, springs 32 attached to the gearbox connect two regions of the gearbox housing 31 that are spaced apart in the axial direction, in particular in the direction of the rotational axis of the rotor shaft of the electric motor 30. In this way, resonant vibrations can be suppressed and the stability and rigidity of the gearbox 31 are increased. The chain wheel 2 engages the chain 1 in a circumferential angular range of more than 90°, in particular and less than 180°, in particular relative to the rotational axis of the chain wheel 2. This enables the chain link to be replaced to be removed even when the chain section is under tension.

[0072] List of reference symbols

[0073] 1 chain

[0074] 2 sprocket

[0075] 3 drifting shaft

[0076] 4 Chain stop device

[0077] 20 driving shaft

[0078] 21 Strut

[0079] 22 Gearbox flange

[0080] 23 Flange part, engine side

[0081] 24 Rotor shaft

[0082] 25 bearing flange

[0083] 26 brake pad carrier, disc-shaped

[0084] 27 Anchor disc

[0085] 28 magnetic bodies

[0086] 29 Release lever

[0087] 30 electric motor

[0088] 31 gearboxes

[0089] 32 springs

[0090] 40 Torque support range

[0091] 41 Center strut

Claims

Patent claims:

1. Geared motor, in particular for a chain conveyor device, wherein the geared motor has a gear driven by an electric motor, wherein the gear flange (22), which receives the bearings for the rotatable mounting of the input shaft (20) of the gear on the gear flange (22), is centered and aligned with the motor-side flange part (23), in particular by a centering collar being formed on the gear flange (22), to which a centering collar of the flange part (23) is applied.

2. Geared motor according to claim 1, characterized in that a torque support area and an output flange are formed on the gear housing, in particular in one piece, wherein struts (21) and a central strut (41) each connect the torque support area to the output flange, wherein the output flange accommodates a bearing of the output shaft of the gear.

3. Geared motor according to one of the preceding claims, characterized in that a cross strut connects the central strut (41) to the struts (21).

4. Geared motor according to one of the preceding claims, characterized in that the central strut (41) is aligned parallel to the axis of rotation of the rotor shaft, and / or that the struts (21) each have a non-zero angular amount to the central strut, in particular have the same angular amount with a different sign to each other.

5. Geared motor according to one of the preceding claims, characterized in that the central strut is arranged in the plane spanned by the struts (21).

6. Geared motor according to one of the preceding claims, characterized in that the cross strut is arranged in the plane spanned by the struts (21).

7. Geared motor according to one of the preceding claims, characterized in that the distance between the struts (21) increases with increasing distance from the output flange, in particular increases strictly monotonically.

8. Geared motor according to one of the preceding claims, characterized in that the axial width of the torque support area, in particular the width of the torque support area measured in the direction parallel to the axis of rotation of the rotor shaft, torque support area, decreases monotonically with increasing distance to the center strut.

9. Geared motor according to one of the preceding claims, characterized in that springs connect two regions of the gear housing which are spaced apart from one another in the axial direction.

10. Chain conveyor device, wherein the chain conveyor device comprises a chain, a sprocket and a geared motor according to one of the preceding claims, wherein the electric motor of the geared motor has an electromagnetically actuated brake on its side facing away from the gearing of the geared motor, wherein the sprocket is connected to an output shaft of the geared motor, in particular in a form-fitting manner, wherein teeth of the sprocket engage in chain links of the chain, in particular for conveying and holding the chain.

11. Chain conveyor device according to one of the preceding claims, characterized in that the chain stop device is fastened to the geared motor and / or that the chain is fixed to a first of its chain links by means of a chain stop device, the chain stop device being fastened to the geared motor.

12. Chain conveyor device according to one of the preceding claims, characterized in that the geared motor has an electric motor, the housing of which encloses and / or surrounds the brake.

13. Chain conveyor device according to one of the preceding claims, characterized in that the brake has a magnetic body which has an annular recess into which an electrically energizable annular winding is inserted, in particular wherein the annular axis of the annular winding is aligned coaxially with the axis of rotation of the rotor shaft, wherein the rotor shaft has external teeth or, in particular, is connected in a rotationally fixed manner by means of a key connection to an annular, externally toothed driver which is plugged onto the rotor shaft, wherein a disc-shaped brake pad carrier is plugged onto the driver and engages with its internal teeth with the external teeth of the driver, in particular so that the brake pad carrier is arranged displaceably in the axial direction, wherein an armature disk is arranged in the axial direction between the brake pad carrier and the magnetic body,which is connected to the magnetic body in a rotationally fixed manner and is arranged to be displaceable in the axial direction, wherein, when the ring winding is energized, the armature disk is drawn towards the magnetic body against the spring force generated by spring elements supported on the magnetic body and pressing on the armature disk, so that the brake pad carrier runs freely, in particular wherein, when the ring winding is not energized, the spring elements press the armature disk onto the brake pad carrier and thus the brake pad carrier is pressed on its side facing away from the magnetic body onto a braking surface which is formed on a flange part or on a sheet metal part which rests on the flange part, or on the motor housing.

14. Chain conveyor device according to one of the preceding claims, characterized in that the chain wheel engages in the chain over a circumferential angular range of more than 90°, in particular of more than 90° and less than 180°, and / or that the release lever is connected via a pivot joint to an axially movably arranged bolt, and / or that the release lever is supported at a pivot point which is arranged on a flange part or bearing flange of the electric motor, wherein the bolt projects through the magnetic body and through a recess in the armature disk and is widened on the side of the armature disk facing away from the magnetic body or is connected to a part for widening in such a way that the bolt is axially limited by means of the widening, and / or that the release lever can be locked by a locking device of the brake, in particular on the magnetic body.

15. Chain conveyor device according to one of the preceding claims, characterized in that the housing of the electric motor, which is in particular designed in several parts, not only houses the stator of the electric motor but also the brake, in particular wherein the release lever protrudes through the housing into the surroundings of the electric motor, and / or that the brake is arranged on the axial end region of the rotor shaft of the electric motor facing away from the gearbox, and / or that Springs connect a first region of the gear housing to a second region of the gear housing, in particular wherein the first region is spaced apart from the second region in the axial direction, in particular parallel to the direction of the axis of rotation of the rotor shaft, in particular wherein the springs are arranged on the outside of the gear housing.

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